Pump



March 16, 1948.

c. w. M oTT PUMP Filed June 3o, 1943 '3 sheets-sheet 1 SUNW blNN BNN A LJQNN NMi .- PMS-pini March 16, 19,48.

C. W. MOTT PUMP Filed Jun so, 1943 5 sheets-sheet 2 NNN March 16, 1948. c, WMOTT -I 2,437,887"

4 Pim? l A Filed June 30, 1943 3 Sheets-Sheet 3 Cari MLM-[5 Patented Mar. i6, i948 `rUMr Carl W. Mott, La Grange, Ill., assigner-to International Harvester Company, a corporation of New Jersey Application June YSi), 1943, Serial No. 492,858

3 Claims. 1

This invention has to do with a hydraulic pump having a plurality of cylinders and `relates particularly to an arrangement in which the cylinersare revolved to cause the reciprocation of cylinders or the equivalent therein. The .present `application is a continuation-impart of my copending application, Serial No. 456,463, filed November 21, 1%2, Patent No. 2,427,871, September 23, 1947.

A general object of the invention is the provision of a slender Acompact multicylinder or chamber pump operable at high speed to deliver liquid at a relatively high pressure.

A further general object is the provision of a pump in which there is a carrier rotatable to revolve pumping chambers thereon having parts reciprocable axially of the carrier to cause expansion and contraction of such chambers, together with novel means yfor imparting reciprocable movement to said parts While .the chambers are revolved.

A still further general object is the provision of a new commutating means containing inlet and outlet channels having ports within an annular sealing surface swept over by ports respectively communicating with the revolving chambers, all coordinately Aarranged Aso the chamber ports successively register communicativeiy with the channel inlet port during chamber expansion and with the channel out-let port during chamber contraction.

These and more specific objects inherent in and encompassed by the invention will be better .understood upon reading the ensuing portion of this specification with reference to the annexed drawings, wherein:

Fig. 1 is a sectional view when axially and and substantially centrally through a pump embodying a preferred form of kthe invention.;

Figs. 2, .3, and 4 are transverse sectional views taken on the lines 2 2, 3-,3,an,d .ll- .4 of Fig. l;

Fig. 5 is a fragmentary sectional view taken .on the line 5--5 of Fig. 1;

Fig. 6 is a perspective View of a commutating member employed in the Fig. 1 embodiment;

Fig. 7 is a View taken similarly to Fig. 1 through a second preferred form;

Fig. 8 is a View taken Vsimile.rly to Fig. l through a third preferred form.; and

Fig. 9 is a sectional view taken .0n the line .9-9 in Fig. 8.

That form of the invention shown in Figs. l to 6, which has been carved out .of the aforesaid copending application, will now .be described. In Fig. 1, the pump, indicated in its entirety by the reference character P, is shown mounted upon a iront side portion of an internal combustion engine E from which it is adapted .to receive driving force. Bolts |80 connect the pump casing 13S..

(Cl. 10S- 162) to a gear casing 82, which is .suitably attached to the engine.

A driving gear |93, driven from an engine part as a valve operating cam shaft IB02, drives a .pinion gear |9| .wedged on a pump shaft |92. This pump shaft is enclosed for a portion of its length by a hollow casting |93 .forming part of the pump casing |S| and on the .outer end of `which .there is a bearing support AHill 'for a ball bearing unit |95 for .the shaft |92. .A secondfcasinsT casting |96, suitably connected to the l.casting |93., supports a ball bearing unit :|181 ihavinga race |93 iitted in the casting and .encircling the pump shaft within a plane .oblique thereto. The second race |99 of the bearing unit |91 has hemispherical bearing members 200 fixed thereto .for estab- 'lishing journaled driving connections with hollow cylindrical pump pistons 20|. These l'bearing members 25S also vhave respective interior hemispherical bearing surfaces 2il2 within and against which head -portions .203 of connecting pins 2M are slidably seated for universal movement. IIhere .are crown openings 2115 in `the hemispherical .bearing members through which the pins 206 4extend .for connection with the plungers 29|.

The plungers 2il|,.of which there are four distributed equidistantly.circumferentially about .the drive shaft T92, are seated within the bores of cast cylinders or chambers 20.5 of which ithepistons constitute parts axially reciprocable .to expand and contract thesame. On-the back end of the shaft |92 (the Vend disposed to the left as viewed in Figure 14) there is a threaded portion 298 to which a disk-shapedcylinder or chamber carrier 209 is rotatably ixed. A .ported member Zl, having vfour axial channels or ports 2|| respectively for the cylinders 206 and communieating therewith through openings 2i|2 in the carrier, is lxed to and for rotation with said carrier. As the parts connected .to the shaft .|92 are rotated, the pistons k211| will .be .complementally actuated by axially compressible springs 2|3 within the pistons and vdiametrically opposite portions of the ball bearing unit that are inclined axially of the carrier to reciprocate in their cylinders for alternately sucking voil in through the ports 2 and forcing it .out lthrough said ports.

Cap bolts 2|3, Figs. 2 and `3, hold the cylinders 2' and the ported block 2|() 4on the carrier. These bolts extend through holes (not shown) in the block 2m and thence through holes 2|3b in the carrier into threaded recesses 2 3c in the block in which the cylinders .2HE are formed.

At the back end of .the pump, there is another casing casting 2id to which is bolted, by means of bolts 2 |55, a stationary cylindrical valve or commutating member 2i6. This commutating member 2|8 has axial intake and discharge ducts 2H and 2id, Figs. i and 5, and the cylindrical exterior of said member forms a sealing surface having a sliding t with the cylindrical center bore through the ported casting 2 l0, facilitating rotation of the latter thereabout while maintaining a iiuid seal contact therewith. While the back ends of the ports 2|| are in registry with a transverse port 2|9 which communicates with the axial intake duct 2| 1 (see Fig. 4), their respectively associated pistons 20| will be receding axially forwardly under the force of their springs 2| 3, as permitted by an inclined portion of the force reaction unit |91 then being traversed, to suck oil inwardly through the ports 2H, and subsequently as the back ends of the ports 2|| associated with the filled cylinders reach registry with a transverse port 220, which communicates with the discharge duct 2|8, their associated pistons will be moving rearwardly under force exerted by the opposite inclined portion of the force reaction unit to expel the oil from said ports 2|| into the discharge duct 2|8. Since the intake slot 2|9 is broader than the diametrically opposite discharge slot 220, an additional slot 22| is provided on the side of the member 2|6 with the narrower'slot 220 so the frictional drag of the rotating casting 2|0 thereon is properly balanced.

To the casting 2|4, there is connected another casting 222 and a plate 223 by bolts 224. Cap bolts 225 connect a multiduct communicating conduit 225 to the plate 223. Fluid as from a reservoir (not shown) is delivered to the pump through an intake passage 226 in the conduit and thence flows through a hole 223- in the plate 223, a hole 222B- in plate 222, and an L- shaped passage 2|4a in the casting 2|4 into the above described axial intake duct 2|1 of the fixed cylindrical valve member 2| 6. During the suction strokes of the pistons 20|, iiuid will be taken into the cylinders 206. After each piston completes its forward suction stroke under the force of its spring 2|3, it is immediately moved rearwardly while recompresslng its spring 2|3 and forcing oil from its cylinder under pressure through the slot 220 and the passage 2|8 in the cylindrical commutating member 2|B, an L- shaped channel 230 in the casting 2|4 past a check valve 23| in a hole 232 in the plate 222, and through a hole 233 in the plate 223 into a high pressure discharge channel 234 in the multichannel conduit 2259.

A thrust bearing unit 235 nested in the left end casting 2| 4 is pressed against by the ported casting 2|0 to prevent axial displacement-of the carrier 209 and the cylinders 206 when the pistons 20| are pressed forwardly incident to traversing the one inclined portion of the oblique reaction bearing unit |91. The end castings |96 and 2I4 are predeterminedly spaced by a cylindrical casing member 236 and are held firmly against the ends of such casing member by long bolts 231 of which one is shown in Fig. 1.

Attention is directed to a by-pass control drive consisting of a gear 238 connected for impositive drive with the shaft |92 by means of a slipclutch device 239, a gear 240 drivable by gear 238, and a counter-shaft 24| drivable by the gear 240 for operating a by-pass valve mechanism encased within lower portions of the plates 222 and 223 but not shown since it is not hereinafter claimed.

The modification shown in Fig. '1 has for the most part elements identical with or corresponding to respective elements of the embodiment shown in Figs. 1 to 6. To expedite this description, those identical or corresponding parts are designated by the same respective reference characters.

One difference that the embodiment in Fig. 'I

has with respect to that in Figs. 1 to 6 is the omission of the counter-shaft 24|, the gearing driving this counter-shaft from the pump shaft |92, the by-pass valve mechanism driven by the counter-shaft, and consequently the plates 222 and 223 in which the by-pass device was encased. Therefore, the plate 2i4 is provided with the inlet passage 2231 and the outlet passage 233. The check valve 23| is omitted from the passage 232. The further detailed difference is the provision of a iiange 2| 6a upon the left end of the commutating block 2|6 for attachment to the casting 2|4, and the proper orientation of the block 2 6 with respect to the pump is maintained by a pin 2|6b inserted through the flange 2|6 into a recess therefor in the casting 254. A flat annular bearing member 235 is substituted for the ball bearing unit 235 in the rst embodiment.

The primary difference between this second embodiment and the first embodiment is in the means employed for maintaining the pistons 20| seated upon the hemispherical bearing studs 200 on the inclined bearing unit |91. This second embodiment dispenses With the springs 2|3, which were used for piston translation in the rst embodiment, and employs instead a plurality of thrust -units 25| comprising hollow members 252 slidable axially `within holes 253 in the carrier 209. The right ends of the members 252 bear constantly against left-end portions of the pistons 20|, against which they are urged by springs 254 which are held under compression by headed members 255 slidable within the members 252 by bearing reactively against a member 256 having a flat inclined face 251 generally parallel with the inclined plane occupied by the bearing unit |91 but being slightly more inclined with respect to the pump axis. The member 256 is fixed at 258 to the commutating member 2|6 so as to remain xed and thereby held against rotation. During rotation of the carrier 209 with the pump shaft |92, the heads 259 of the members 255 slide about a peripheral edge portion of the inclined face 251 while rocking radially with respect to said face as facilitated by curved surface portions 26| of these heads 259. As mentioned hereinabove, the plane of the face 251 on the ilxed member 256 is slightly more inclined with respect to the pump axis than the plane occupied by the inclined bearing unit |91. The reason for this is that the centers of the pistons 20| are farther from the pump axis than the centers of the reciprocal units 25|, but since it is essential for these units 25| to have the same length of reciprocal stroke as the pistons, the axial displacement of the annular path about the edge of the surface 251 must be the same as that of the pistons 20| though a shorter radial distance from the pump axis. The operation of the pump shown in Fig. 7 is the same as that described above with respect to the pump shown in Figs. 1 to 6.

A third embodiment of the invention shown in Figs. 8 and 9 is also generally like the embodiment shown in Figs. 1 to 6, wherefore the same expedient is followed of designating the same or corresponding parts by the same respective reference characters.

In this embodiment a third means is employed for urging the pistons 20| toward and maintaining them in, seated relation with the hemispherical bearings 200 upon the inclined bearing unit I91. This means includes cylindrical plunger members 26E which are slidably disposed within holes 262 in the cylinder carrier 209, respectively beside the port holes 2 l 2 in the carrier as is illustrated in Fig. 9. The ported member 2l@ is provided with oversized recesses 263 for receiving the left-end portions of the plungers 26 l. Radial channels 264 in the left end face of the carrier` 209 communicate respectively between the recesses 263 and a chamber 265 formed between the right end of the commutating block 2i6 and a central left-end portion of the carrier. Fluid under pressure from the high pressure outlet channel 2I8 is introduced into the chamber 265 through a channel 269 in the member 2l6, and this high pressure fluid is forced radially outwardly through the channels 264 into the recesses 263 to apply a force upon the left ends of the plungers 26i for urging them and the cylinders 20! with which they abut to the right for maintaining the cylinders seated upon the hemispherical bearings 200.

While I have herein shown and described a limited number of embodiments with the view of illustrating the invention, it should be understood that the invention extends to other forms, arrangements, structures and details falling within the scope and spirit thereof and not sacrificing all of its material advantages.

What is claimed is:

1. In a pump, a rotatable carrier having a radially extending web-like body, cylinders on one end of the carrier body with their axes generally parallel with the rotational axis of the carrier and revolvable about said axis pursuant to carrier rotation, pistons reciprocable in said cylinders to cause expansion and contraction of the space therein, cylinder ports leading through the carrier to the opposite end of the carrier body, commutating means having inlet and outlet ports successively communicatively traversed by the cylinder ports respectively during expansion and -contraction of the space in their associated cylinders, an annular force-reaction member encircling the carrier axis at the one end of the carrier within a plane oblique thereto to incline diametrically opposite edge portions of said member axially of the carrier, and means for pressing said pistons axially toward said reaction member to cause the pistons to alternately traverse said inclined edge portions and thereby incur the reciprocation of the pistons, the last-named means including a member having an annular force-reaction portion encircling the carrier axis at the other end of the carrier within a plane -generally parallel with the iirst-named plane, and axially reciprocable thrust members extending axially through the carrier body between the pistons and said annular force-reaction portion.

2. In a pump, a rotatable carrier having a radially extending web-like body, cylinders on one end of the carrier body with their axes generally parallel with the rotational axis of the carrier and revolvable about said axis pursuant to carrier rotation, pistons reciprocable in said cylinders to cause expansion and contraction of the space therein, cylinder ports leading through the carrier to the opposite end of the carrier body, commutating means having inlet and outlet ports successively communicatively -traversed by the cylinder ports respectively during cylinder expansion and contraction of the space in their associated cylinders, an annular force-reaction member encircling the carrier axis at the one end of the carrier within a plane oblique thereto to incline diametrically opposite edge portions axially of the carrier, and means for pressing said pistons axially toward said reaction member to cause the pistons to alternately traverse said inclined edge portions and thereby incur the reciprocation of the pistons, the last-named means including axially reciprocable thrust members extending axially through the carrier body into respective thrust-applying relation with the pistons, and chamber means at said other end of the carrier into which ends of said thrust members project, and said chamber means being communicative with the commutating means outlet port to receive fluid therefrom under pressure for forcing the thrust members into said thrust-applying relation with the pistons.

3. In a pump, a rotatable carrier having a radially extending body, pump chambers carried on said body in radially spaced relation from the carrier rotational axis, the principal axes of said chambers being substantially in parallelism with the carrier axis, wall portions of said chambers disposed toward one end of said body being displaceable axially of the respective chambers for expanding and contracting the same pursuant to such movement, each of the said chambers having a port-like channel leading through the carrier body to the opposite end thereof, commutating means having inlet and outlet ports successively commutatively traversed by said channels respectively during chamber expansion and contraction, an annular forcereaction member encircling the carrier axis at said one end of the carrier within a plane oblique thereto to incline diametrically opposite edge portions of said member axially of thecarrier, and means for urging said chamber wall portions axially toward said reaction member to cause said Wall portions to alternatively traverse and react upon said inclined edge portions and thereby incur axial reciprocation of such wall portions in predetermined phase relation with the traversal of said commutating means by said channels, and said pressing means including axially reciprocable thrust members extending axially through the carrier body in sealing relation therewith and into said chambers into respective thrust-applying relation with said wall portions, and means at the other end of said carrier body for applying pressure against said thrust members for urging them and their associated chamber wall portions toward said reaction member.

CARL W. MOTT.

REFERENCES CITED The following references are of record in the le of this patent:

UNITED STATES PATENTS Number Name Date 1,340,447 Ingolby May 18, 1920 1,822,064 Sorensen Sept. 8, 1931 1,908,612 Johnson May 9, 1933 1,945,391 Benedek Jan. 30, 1934 Y1,970,133 Ferris, et al. Aug. 14, 1934 2,081,477 Egersdorfer May 25, 1987 2,161,143 Doe, et al. June 6, 1939 2,168,658 Thomas Aug. 8, 1939 2,241,701 Doe May 13, 1941 2,299,235 Snader, et al Oct. 20, 1942 2,331,694 Jeffrey Oct. 12, 1943 

